Heat exchanger



H. G. MELCHE R HEAT EXCHANGER July 4, 1933.

Filed Sept. 9, 1932 4 Sheets-Sheet l INSTQR 4%,

July 4, 1933.

H. G MELCHER HEAT EXCHANGER Filed Sept. 9, 1932 4 Sheets-Sheet 2 INVENTOR y 4, 1933- H. G. MELCHER 1,916,768

HEAT EXCHANGER Filed Sept. 9, 1932 4 Sheets-Sheet 3 ll l llll i In H 1' I \fi I|1|/" Ill/Ill! 2e 2e 2e INVENTOR I July 4, 1933. H. G. MELCHER 1,916,768

HEAT EXCHANGER Filed Sept. 9, 1952 4 Sheets-Sheet 4 40 IINVENTOR 1 to a boiler or other container.

Patented July 4, 1933 UNITED ,sTATEs manure. MELCHER, oreitovn CITY, rENNsYLvAnIA, ASSIGNOR or oNE-nnLr fro 1,916,768 ENT OFFICE JOHN G. cr nnn'rn'nns, or enovn CITY, PENNSYLVANIA I HEAT EXCHANGER App1ication filed September 9, 1932. Serial No. 632,353.

This invention relatesto improvement-sin heat exchangers, more particularly to devices providing forexchange of heat between separate and independent flowustreams, ;to either efiect a cooling of one of the streams, .as tor example, oil, or the heating of the stream where it is desired to pre-heat liqu d flow ng It is among the objects of the invention to provide a heat exchanger of simple, compact and durable construction which shall consist of a plurality ofcast sections of like construction which are joined innumbers determined by the capacity it is desired to obtainin' the'heat exchanging unit. I

A further object of the invention is the provision of a flow system in a -heat exchange device which shall be highly eiiicient in its operation, which shall he designed to set up turbulence bysplitting the flow in the flow system and which shall be further designed to direct the flow of theflnids relative to each other insuch manner as to produce the most efficient exchange of heat. Z

A further object of the invention is the provision of means for providing for the complete submersion of one of the flow channels in the other wherebyone of the flow streams completely surrounds the other flow stituting a part hereof in wl ich like refer-J stream, and still a further object of theinvention is the provision of means for regulating the flow of fluids from the communicating ports through the flow passages in a manner to produce maximumturbulence in the flow stream. 7 p

These and other objects of, the invention will become more apparent from a consideration of the accompanying drawings v con ence characters designate like parts and which Figure 1 1s a longitudinal sect onal View of a heat exchanger embodying the principles of this invention Flgure 2a cross-sec tional view thereof taken along the line IIII of F igure 1 ;'Figure 3 a cross-sectional view'taken along the-line In -III of Figure 1;'Figure 4 an end elevational view of a modified formolthe inventiong Figure 5 a cross-sectional view taken along the line VV offFigure a; Figure 6 an end elevational view of still another modification'of which Figures 7 and '8 are cross-sect onal views taken along the lines VII,VII and VIII-VIII of Figure 6;-Figure 9 anend elevation-a1 view of still another form of the invention of which Figures 10 and 11 are cross sections taken along the lines anclXL-XI of'Figure 9; Figure 12 a crosssectionalgview of a plurality of assembled sectionsof modified form of the plate shown in Figure 1;v Figure 13 an end elevational view of a spiral form; and Figures 14 and 15 an end elevational and cross-sectional view, respectively, of still another type of plate.

l Vith'reference to the structure shown in Figuresl to 3 of the drawings, theelements therein illustrated comprise a series of plates generally designated by thev reference nu- .nieral 1, the plates being preferably cast and having cored-out passages-2 of annular form and axial passages 3, the passages 2 being rendered communicative through aseries of ports 4 and through vent openingsz5. The cast plates 1 areassembled intheiman ner shown in Figure 1 by mounting them on I a threaded stud or rod 6, therebeingas many of the plates assembled together as are nec essaryto providesuflicient capacity toeife'ct a suitable exchange of heat at a given rate of flow ofthe fluidin a manner to; beherejacent plates and by arranging their ports 4, 180 apart, the annular passages 2 are rendered communicative with the end passages 74; and'8al, Thethr0ugh passages3 communicate With the end passages 7 b and 8b.

In operation, the heat exchanging unit is connected with the ports 8a communicating wlth the source of fluid, such as 011, as for example in an automotive vehlcle engine,

and the port 86 is connected to a source of cooling water such as the radiator of an automotive vehicle englne- When so connected,- the fluids will pass under the pressure of the pump inlthe sys- 1 tem through their respective flow passages,

the oil fiowing through the port 7a. into the port 4 of the annular passages 2 and from, one annular passage to another through successive ports 4 until it passes through the opposite port Sal-back into the lubricating system. Similarly, the cooling medium or water flows in at one of the ports 8b.and along and around the axial flow-passages 3 and out through the other port 8?).

The vents 5 prevent the flow passage 2 from being air bound .and further permit draining the unit when its application to another kind of fluid is desired.

With reference to the structure shown in Figures 4 and 5 of the drawings, the inlet and outlet ports are illustrated by the reference numerals 11 and 12, respectively, and it is to be noted that the ports are on the outside of the plates so as to assure that there will be no intermingling of the fluid passing through the respective conduits. In the structure of Figures 4'and 5 the annular flow passages 13, 13a and 13b and the'axial flow passages 14 are arranged'in a manner similar to the passages-2 and 3 of Figures 1, 2, 3, inclusive, of the drawings, being however a multiple of passages which "are inter-communicating through common flow chambers 15 and 16p The flow of the fluid entering f the port 11 is radially inward toward the annular passages 13, 13a and 13?), as indicated by the arrows and the location of' the flow chambers 15 and 16 on opposite sides of the annular passages causes the flow to be divided in two directions. By gradually reducing the width of the flow chamber 15 and gradually increasing the width of the flow chamber 16 the fluid will flow at substantially equal velocities through the several annular passages 13, 13a and13b. The dividing of the flow in the manner indicated causes a turbulence of the fluid which is desirable in that it assures proper circulation of the fluid through the. heat exchanger plates and also makes for a more eflicient exchange of heat between the fluid in the annular passages and thefluid in the axial-passages.

In Figures 6 to 8 inclusive of the drawings,

" the flow passages 17 and 17a communicate spective flow passages.

WVith reference to the structures disclosed V in Figures 9 to 11 inclusive of the drawings,

the tubular passages 21 and 21a communicate with a flow chamber 22 which constitutes a passage between annular passages 21 and 21a. Ports 24 and'25 are provided to con stitute-inlets or outlets as the case may be and if the fluid is directed to enter the port 24 it will flow through divided paths in the annular passage 21, thence to the flow chamaxially disposed passages of' the cooling or heating medium, as the case may be.

' It will be noted in'Figure 10 that'the'annular flow passages 21 and 21a are relatively small in proportion to the ports 24 and 25 and for this reason the flow of oil or the like to the annular passages is uniformly divided and turbulence is produced where the flow streams meet.

In Figure 12 of the drawings, the plates 28 are formed with annular slots or grooves 29 which are open at one end and whichwhen assembled in the manner shown, form annular flow passages. Gaskets 30 are disposed between the plates and are cut out as at 31 to correspond to the grooves 29 and other flow passages. 1 I

Plates 28 are provided with ports 32 which when staggered 180 apart cause a divided flow through the annular passages 29, as hereinbefore explained. Plates 28 are provided with axial flow passages 33 and 33a.

In Figure 13 of the drawings, the flow channel 34 is in the shape of a spiral with ports 35 and 36 at the respective ends thereof. Ribs or webs 37 connect the flow channel with the outer wall 38. This type is less efiicient than the annular type .of flow channel as the flow is in one direction because of the location of the ports at the ends thereof.

WVith referencetoFigures 14 and 15 of the drawings, the plates illustrated are similar to the plates of Figures 4 to 8 of the drawings in that the annular flow channel .39 is completely surrounded by the fluid of the axial channel 40. A single annular channel is employed instead of the multiple channels of the structures shown in Figures 4 to 8 of the drawings. v V

In the structures disclosed in Figures 1 and 12 of the drawings, the annular flow passages are surrounded on two sides by the medium flowing axially of the unit, and in the remainingfigures of the drawings the annular flow passages are completely surrounded by the fluid with which it is desired to effect the exchange of heat'with the fluid in the annular passages. It is, of course, obvious that the latter construction is more efficient and would be productive of a higher rate of exchange of heat within a given space.

exception of that of Figure 13, in which the flow passages are spiral, the inlet and outlet orts are located in such manner that the ow to the annular passages is in opposite directions which increases the efiiciency, and furthermore causes a turbulence of the fluid in the annular passages adjacent the ports at the point where the flow streams meet. The turbulence in the fluid is a desirable feature since the agitated fluid effects a greater exchange of heat with its surrounding wall, and with the-construction herein employed, turbulence is attained to a high degree.

, From the multifarious designs herein dis closed in the numerous figures of the drawings, it is apparent that the principle of the invention is applicable to a large number of forms, and applicant doesnot wish to be limited to the specific forms herein disclosed as various modifications may be made in the details of construction without departing from the principles herein set forth.

On account of the compactness of the ex-' change unit and the construction of the plates which in most cases may be cast, but which may be constructed in any other manner, a

heat exchanger of relatively large heat exchange capacity may be constructed within a suiiiciently restricted space to be applicable for use in the cooling of the lubricatingoils for automobile vehicle engines and for other kindred uses such as the cooling of transformer oils and the like.

Although the invention has been described as for use in cooling oils or the like, it will obviously be applicable for heating purposes or for any use where it is designed to effect an exchange of heat between two streams of liquid or gases as the case may be.

I claim:

1. A heat exchanger comprising a plate having an annular flow passage therein in heat exchange relation with-one or more axial passages, said annular passage having communicating inlet and outlet ports in staggered relation whereby the flow of fluid is divided in said passages and said annular and axial passages having connections at the ends of said plate for sources of fluid supply.

'2. A heat exchanger comprising a plate having one or more annular passages and axial passages disposed between said annular passages, said annular passages having ports spaced to cause fluid to flow in divergent paths and said axial passages being communicative around the walls of said annular passages whereby the fluid flowingaxially of said exchanger plates completely surrounds the wall of the annular flow passages.

3. A heat exchanger comprising a'plate having annular passages in radially spaced relation and having axially disposed passages between said annular passages, said annular passages being isolated'from said axial passages and having connecting flow chamwhereby said annular passages are completely surrounded by the fluid flowing in said; axial passages and the inlet and outlet ports of said annular passages being in spaced relation. whereby the fluid is divided in its flow from the inlet passages to the outlet passages and whereby the fluid is subj ected to turbulence. I

5. A heat exchanger comprising a plurality of plates having annular flow passages in radially spaced relation, said passages com- -municating at one end by a flow chamber and having ports at the'other end, axial passages disposed between said annular passages and radial passages communicating with said axial passages whereby the annular passages are completely -surroundedby the fluid passing through the axial passages, the ports .of said annular passages being s0 arranged that the fluid flowing into one port will be divided and flow through the annular passages, thence through the flow chamber between the annular passages, and again through the annular passages to the outlet port.

6. A heat exchanger comprising a flow channel in the form of a series of annular passages, each passage having inlet and outlet ports communicating. with the next adjacentpassages, and all of said annular passages havlng common axially disposed passages and in heat exchange relation therewith, the inlet and outlet ports of said annular pas-- sages being spaced to divide the flow into divergent paths through said annular pas sages.

7. A heat exchanger comprising a flow channel in the form of a series of annular passages, each passage having inlet and out let ports communicating with the next adja- 1 cent passages, and all of said annular pas- III means in said end plates for connecting the r same! to fluid circulating systems whereby one fluid flows an 'ularly through said an nular flow channel and another fluid flows .in a substantially straight line through said axial flow passages.

Intestimony whereof I have hereunto set 

